CN103975143A - Gas turbine cooling system and gas turbine cooling method - Google Patents
Gas turbine cooling system and gas turbine cooling method Download PDFInfo
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- CN103975143A CN103975143A CN201280044710.3A CN201280044710A CN103975143A CN 103975143 A CN103975143 A CN 103975143A CN 201280044710 A CN201280044710 A CN 201280044710A CN 103975143 A CN103975143 A CN 103975143A
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- 238000001816 cooling Methods 0.000 title claims abstract description 86
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 38
- 238000011084 recovery Methods 0.000 claims abstract description 33
- 229920006395 saturated elastomer Polymers 0.000 claims abstract description 30
- 230000001105 regulatory effect Effects 0.000 claims description 5
- 238000011144 upstream manufacturing Methods 0.000 claims description 4
- 239000007789 gas Substances 0.000 abstract description 95
- 239000002918 waste heat Substances 0.000 abstract description 4
- 238000010438 heat treatment Methods 0.000 description 8
- 239000002826 coolant Substances 0.000 description 6
- 239000002912 waste gas Substances 0.000 description 6
- 238000000034 method Methods 0.000 description 5
- 238000000926 separation method Methods 0.000 description 5
- 230000006837 decompression Effects 0.000 description 4
- 238000010276 construction Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 238000005516 engineering process Methods 0.000 description 3
- 239000002737 fuel gas Substances 0.000 description 3
- 239000006200 vaporizer Substances 0.000 description 3
- 239000000112 cooling gas Substances 0.000 description 2
- 230000007812 deficiency Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000005611 electricity Effects 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 239000012808 vapor phase Substances 0.000 description 2
- 230000002159 abnormal effect Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 235000014171 carbonated beverage Nutrition 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 239000000498 cooling water Substances 0.000 description 1
- 230000007797 corrosion Effects 0.000 description 1
- 238000005260 corrosion Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 238000005755 formation reaction Methods 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 230000020169 heat generation Effects 0.000 description 1
- 230000002401 inhibitory effect Effects 0.000 description 1
- 238000010248 power generation Methods 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
- F02C6/18—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use using the waste heat of gas-turbine plants outside the plants themselves, e.g. gas-turbine power heat plants
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
- F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
- F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
- F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
- F02C7/12—Cooling of plants
- F02C7/16—Cooling of plants characterised by cooling medium
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2220/00—Application
- F05D2220/30—Application in turbines
- F05D2220/31—Application in turbines in steam turbines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2260/00—Function
- F05D2260/20—Heat transfer, e.g. cooling
- F05D2260/207—Heat transfer, e.g. cooling using a phase changing mass, e.g. heat absorbing by melting or boiling
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2260/00—Function
- F05D2260/20—Heat transfer, e.g. cooling
- F05D2260/232—Heat transfer, e.g. cooling characterized by the cooling medium
- F05D2260/2322—Heat transfer, e.g. cooling characterized by the cooling medium steam
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E20/00—Combustion technologies with mitigation potential
- Y02E20/16—Combined cycle power plant [CCPP], or combined cycle gas turbine [CCGT]
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E20/00—Combustion technologies with mitigation potential
- Y02E20/16—Combined cycle power plant [CCPP], or combined cycle gas turbine [CCGT]
- Y02E20/18—Integrated gasification combined cycle [IGCC], e.g. combined with carbon capture and storage [CCS]
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
Abstract
The invention provides a gas turbine cooling system and a cooling method, which can efficiently cool a gas turbine by using high-pressure steam generated by a waste heat recovery boiler or reducing the generation of the high-pressure steam without generating a situation. The cooling system is provided with: a gas turbine (3); an exhaust heat recovery boiler (2) having a high-pressure system (6) that generates high-pressure steam by exchanging heat with exhaust heat from the gas turbine (3), a high-pressure drum (11) that supplies water and steam to the high-pressure system (6), an intermediate-pressure system (7) that generates intermediate-pressure steam by exchanging heat with exhaust heat from the gas turbine (3), and an intermediate-pressure drum (12) that supplies water and steam to the intermediate-pressure system (7); an intermediate-pressure steam pipe (19) that connects the intermediate-pressure system (7) to the cooling system of the gas turbine (3) and that supplies intermediate-pressure steam from the intermediate-pressure system (7) to the cooling system; and a steam supply pipe (20) which connects the high-pressure drum (11) and the intermediate-pressure drum (12) and supplies saturated steam in the high-pressure drum (11) from the high-pressure drum (11) to the intermediate-pressure drum (12).
Description
Technical field
The present invention relates to utilize the steam being produced by heat recovery boiler to carry out cooling gas turbine cooling system and gas turbine cooling means to gas turbine.
Background technique
The heat recovery boiler utilization of being located at gas turbine combined cycle generating (GTCC), gasifying combined generating (IGCC) produces the steam for driving steam turbine from the used heat of gas turbine.But, be accompanied by the high temperature of the gas turbine of seeking high efficiency, from the viewpoint of equipment protection, need to carry out cooling to tail pipe and other positions etc. of the gas turbine burning that becomes high temperature in the running.Therefore, in above-mentioned power generation system, cooling for gas turbine is carried out, not only use air as cooling medium, and sometimes use the steam being produced by heat recovery boiler as cooling medium.
Such technology is disclosed in patent documentation 1: occurred in the running abnormal, by the high compressed steam of heat recovery boiler or middle pressure steam are imported to vapor cooling system, maintain cooling based on steam.
The technology of the cooling control of the high-temperature components such as the burner of simultaneously realizing the gap control between moving vane and the blade ring portion of being undertaken by steam and undertaken by steam is disclosed in patent documentation 2.
Formerly technical paper
Patent documentation
Patent documentation 1: Japanese kokai publication hei 10-37711 communique
Patent documentation 2: TOHKEMY 2002-4807 communique
Summary of the invention
The problem that invention will solve
Because the 4.0MPa producing in heat recovery boiler conforms to the desired cool condition of the object that is cooled (gas turbine) to the middle pressure steam of 5.0MPa left and right, therefore, in the case of using the steam being produced by heat recovery boiler as cooling medium, in use, press steam more.
On the other hand, in order to improve device efficiency, require to increase the high compressed steam amount that produced by heat recovery boiler, therefore, require to reduce cooling used necessary vapor volume poor of the middle pressure vapor volume being produced by heat recovery boiler and the object (gas turbine) that is cooled as far as possible.But, consequently, according to the difference of load of electrical generation, fuel condition, in may producing, press vapor volume, with respect to the necessary vapor volume of the object that is cooled, not enough situation occur.
Therefore, consider a part for the high compressed steam producing in heat recovery boiler to be used as cooling medium, but expressly the steam of high temperature, high pressure is carried out to desuperheat, decompression, probably cause device efficiency to reduce.
The present invention makes in view of above-mentioned situation, the situation that the high compressed steam that a kind of use produces by heat recovery boiler is provided or reduces the generation of high compressed steam there will not be, and can utilize expeditiously steam to carry out cooling gas turbine cooling system and gas turbine cooling means to gas turbine.
For solving the means of problem
In order to solve above-mentioned problem, gas turbine cooling system of the present invention and gas turbine cooling means adopt following means.
The gas turbine cooling system of the first scheme of the present invention possesses: gas turbine; Heat recovery boiler, its have carry out heat exchange with the used heat from gas turbine and produce the first system of the first steam, to the first system for feedwater and the first drum of steam, carry out heat exchange with the used heat from gas turbine and produce than the second system of the second steam of the first steam low pressure, the second drum to second system for feedwater and steam; The first stream, it is connected second system with the cooling system of gas turbine, supply with the second steam from second system to cooling system; The second stream, it is connected the first drum with the second drum, supply with the saturated vapor in the first drum from the first drum to the second drum.
According to the gas turbine cooling system of above-mentioned the first scheme, the water of the second drum and steam are supplied with to the second system of heat recovery boiler, in second system Yu from the used heat of gas turbine, carry out heat exchange and produce the second steam.The second steam is the supply of the cooling system from second system to gas turbine via the first stream, thereby carries out cooling to gas turbine.In addition, the saturated vapor in the first drum is supplied with to the second drum from the first drum via the second stream.Consequently, can make the vapor volume of the steam of supplying with from the second drum to second system increase, therefore, also can make the vapor volume of the steam of the cooling system supply from second system to gas turbine increase.
The gas turbine cooling system of above-mentioned the first scheme can be also, also possesses vapor volume regulating mechanism, and the state of cooling of this vapor volume regulating mechanism based on gas turbine is adjusted at the vapor volume of saturated vapor mobile in the second stream.
According to this structure, corresponding to the cooling condition of gas turbine, the vapor volume of the saturated vapor of supplying with to the second drum from the first drum via the second stream changes, and therefore, can supply with the saturated vapor that gas turbine is carried out to cooling required appropriate amount to the second drum.Can for example, by the vapor volume of the cooled steam of gas turbine the outlet temperature of gas turbine being monitored, managed, discharges based on the cooling system from gas turbine in gas turbine side etc., indirectly judge the cooling condition of gas turbine.
The gas turbine cooling system of above-mentioned the first scheme can be also, is provided with water separator in the downstream of the second stream and in the upstream of the second drum or the second drum.
According to this structure, because the saturated vapor of supplying with to the second drum from the first drum via the second stream utilizes water separator to be separated into water and steam, therefore, isolated steam can be supplied with to gas turbine cooling system, can be utilized water-free steam to carry out cooling to gas turbine.Consequently, can prevent the burn into breakage of the cooling system being caused by the contained water of steam.In addition,, because of the situation that in steam condensing the second drum, water level rises at short notice, therefore, can not suppress the fluctuation of water table of the second drum.
The gas turbine cooling means of alternative plan of the present invention is the gas turbine cooling means of gas turbine cooling system, and this gas turbine cooling system possesses: gas turbine; Heat recovery boiler, its have carry out heat exchange with the used heat from gas turbine and produce the first system of the first steam, to the first system for feedwater and the first drum of steam, carry out heat exchange with the used heat from gas turbine and produce than the second system of the second steam of the first steam low pressure, the second drum to second system for feedwater and steam, this gas turbine cooling means possesses: the cooling system from second system to gas turbine is supplied with the step of the second steam; Supply with the step of the saturated vapor in the first drum from the first drum to the second drum.
Invention effect
According to the gas turbine cooling means of above-mentioned alternative plan, the situation that uses the high compressed steam being produced by heat recovery boiler or the generation that makes high compressed steam to reduce there will not be and can utilize expeditiously steam to carry out cooling to gas turbine.
Brief description of the drawings
Fig. 1 represents the Waste Heat Recovery System (WHRS) of one embodiment of the present invention and the summary construction diagram of gas turbine cooling system.
Fig. 2 is the summary construction diagram that represents the gas turbine cooling system of this mode of execution.
Fig. 3 represents Waste Heat Recovery System (WHRS) in the past and the summary construction diagram of gas turbine cooling system.
Embodiment
Below, with reference to accompanying drawing, embodiments of the present invention are described.
The Waste Heat Recovery System (WHRS) of one embodiment of the present invention and gas turbine cooling system are for example applied to the equipment 1 of gas turbine combined cycle generating (GTCC), the gasifying combined generating (IGCC) etc. with heat recovery boiler 2 and gas turbine 3.
Gas turbine cooling system for example by heat recovery boiler 2, gas turbine 3, from the medium voltage network 7 of heat recovery boiler 2 to press gas turbine 3 is supplied with the middle pressure steam pipe 19 (the first stream) of steam, from high pressure drum 11 to pressure drum 12 supply with the formations such as the steam supplying pipe 20 (the second stream) of saturated vapor.
Heat recovery boiler 2 is supplied with road 14 via waste gas and is supplied to the waste gas of discharging from gas turbine 3.And heat recovery boiler 2 carries out heat exchange and generates steam with the heat (used heat) of waste gas.As shown in Figure 1, be provided with such as re-heating subsystem 5, high-pressure system 6, medium voltage network 7, low service system 8, high pressure drum 11, middle pressure drum 12 and low pressure drum 13 etc. at heat recovery boiler 2.
In heat recovery boiler 2, dispose successively re-heating subsystem 5, high-pressure system 6, medium voltage network 7, low service system 8 along the flow direction of waste gas.Re-heating subsystem 5 comprises reheater, and the steam of extracting out from steam turbine 4 is supplied with to re-heating subsystem 5 via cold reheat steam pipe 15, is heated by the reheater of re-heating subsystem 5.Supplied with to steam turbine 4 via high temperature reheat steam pipe 16 by the warmed-up steam of re-heating subsystem 5, thereby steam turbine 4 is driven.
High-pressure system 6 comprises high-pressure superheater, high pressure evaporator, and the high pressure evaporator of high-pressure system 6 is supplied feedwater from high pressure drum 11.The water of supplying with from high pressure drum 11 is heated by the high pressure evaporator of high-pressure system 6, thereby generates steam.The steam generating is heated by high-pressure superheater, thereby generates high compressed steam.The high compressed steam generating is supplied with to steam turbine 4 via high compressed steam pipe 17, thereby steam turbine 4 is driven.
Low service system 8 comprises low pressure evaporator, low-pressure superheater, and the low pressure evaporator of low service system 8 is supplied feedwater from low pressure drum 13.The water of supplying with from low pressure drum 13 is heated by the low pressure evaporator of low service system 8, thereby generates steam.The steam generating is overheated by low-pressure superheater, thereby generates low-pressure steam.The low-pressure steam generating is supplied with to steam turbine 4 via low-pressure steam pipe 18, thereby steam turbine 4 is driven.
Medium voltage network 7 comprises middle pressure vaporizer, middle pressure superheater, and the middle pressure vaporizer of medium voltage network 7 is therefrom pressed drum 12 for feedwater.Therefrom press the water that drum 12 is supplied with to be heated by the middle pressure vaporizer of medium voltage network 7, thereby generate steam.The steam generating is overheated by middle pressure superheater, thereby presses steam in generating.All or part of of the middle pressure steam generating supplied with to the cooling system of gas turbine 3 via middle pressure steam pipe 19, thereby carries out cooling to corresponding site.The cooling system of gas turbine 3 is for example located at the high-temperature part of tail pipe, the unit room etc. of the burner arranging at gas turbine 3.The state of cooling of the necessary vapor volume of therefrom pressing the middle pressure steam that drum 12 supplies with to gas turbine 3 via middle pressure steam pipe 19 based on gas turbine 3 adjusted.Be provided with control valve 25 at middle pressure steam pipe 19, vapor volume is adjusted.
The vapor volume of the gas turbine 3 cooled steams of the outlet temperature of gas turbine 3 being monitored, being managed, for example discharges based on the cooling system from gas turbine 3 in gas turbine 3 sides, temperature, pressure etc., judge the state of cooling of gas turbine 3 indirectly.For example, in the situation that being judged as gas turbine 3 cooling deficiency, by control valve 25 to open sides adjustment, thereby increase the vapor volume of the middle pressure steam of supplying with to the cooling system of gas turbine 3.On the other hand, being judged as gas turbine 3 exceedingly cooling in the situation that, control valve 25 is adjusted to locking side, thereby in reducing, pressed the vapor volume of steam.
Steam supplying pipe 20 from high pressure drum 11 to pressure drum 12 supply with saturated vapor.Be only judged as the middle pressure vapor phase that relies on the water based on therefrom pressing drum 12 to supply with to generate in medium voltage network 7 not enough for the cooling needed vapor volume of gas turbine 3, via steam supplying pipe 20 from high pressure drum 11 to pressure drum 12 supply with saturated vapor.Thus, can utilize from high pressure drum 11 to the steam supplied with of pressure drum 12 make up the middle pressure steam of supplying with to the cooling system of turbine 3.
Cooling the used steam of gas turbine 3 is for example supplied with and is re-used in the driving of steam turbine 4 to high temperature reheat steam pipe 16.
Gas turbine 3 is by making fuel gas drive turbine and the main shaft linking with generator being rotated together with turbine, thereby makes generator drive and generate electricity.Fuel gas in gas turbine 3 after burning is discharged as waste gas.Gas turbine 3 is because the burning of fuel gas becomes high temperature, and therefore, in order to reduce the impact of heat generation, and it is cooling to utilize cooling medium to carry out.Cooling medium for example uses the steam being generated by heat recovery boiler 2.
Steam turbine 4 is supplied to the steam being generated by heat recovery boiler 2, and turbine is driven.The main shaft of steam turbine 4 and generator link, and by rotating together with turbine, generator drive are generated electricity.It should be noted that, with regard to generator, can, by a generator and gas turbine 3 and steam turbine 4 the two links, also can on gas turbine 3 and steam turbine 4, link respectively different generators.
In the example shown in Fig. 1, steam turbine 4 is supplied to respectively reheat steam, high compressed steam, low-pressure steam, thereby turbine is driven from re-heating subsystem 5, high-pressure system 6, the low service system 8 of heat recovery boiler 2.
Next,, with reference to Fig. 2, the gas turbine cooling system of present embodiment is described.
In the present embodiment, be provided with the steam supplying pipe 20 that high pressure drum 11 (the first drum) and middle pressure drum 12 (the second drum) are linked.As shown in Figure 2, steam supplying pipe 20 comprises control valve 21, flowmeter 22, throttle orifice 23, water separator 24 etc.
The control valve 21 of steam supplying pipe 20 carries out on-off action according to the instruction of the control valve of middle pressure steam pipe 19 25.In gas turbine 3 cooling, in the case of utilizing the steam deficiency being generated by medium voltage network 7, supply with the saturated vapor in high pressure drum 11 via steam supplying pipe 20 to middle pressure drum 12.From high pressure drum 11 to the vapor volume of the saturated vapor supplied with of pressure drum 12 decide based on mobile vapor volume in middle pressure steam pipe 19.
For example, be only judged as the middle pressure vapor phase that relies on the water based on therefrom pressing drum 12 to supply with to generate in medium voltage network 7 not enough for the cooling needed vapor volume of gas turbine 3, by control valve 21 to open sides adjustment, thereby make saturated vapor vapor volume increase.On the other hand, being judged as when exceedingly cooling to gas turbine 3, control valve 21 is adjusted to locking side, thereby the vapor volume of saturated vapor is reduced.
Flowmeter 22 is located at steam supplying pipe 20, for being determined at the vapor volume of the mobile saturated vapor of steam supplying pipe 20.Throttle orifice 23 is located at the back segment of the control valve 21 in steam supplying pipe 20.The decline sharply of the pressure of throttle orifice 23 energy inhibitory control valves 21, can reduce the collision of the saturation water to control valve 21 being produced by steam mobile in steam supplying pipe 20.Consequently, can prevent breakage, the corrosion of control valve 21.It should be noted that, for the fault that the water that prevents from producing causes, also can interference plate be set at the back segment of throttle orifice 23 in the time utilizing throttle orifice 23 to reduce pressure to saturated vapor.
Water separator 24 is located at the downstream side of steam supplying pipe 20 and is arranged in the upstream side or middle pressure drum 12 of middle pressure drum 12.Water separator 24 from saturated vapor mobile steam supplying pipe 20 by steam and liquor separation.Water separator 24 can be make fluid by wire netting or corrugated sheet make steam and liquor separation mode, utilize centrifugal force to make the any-modes such as the mode of steam and liquor separation.The steam that separation obtains is directly supplied with to medium voltage network 7, separates the liquid obtaining and is temporarily stored in middle pressure drum 12.
In the situation that water separator 24 is not set, a part for the saturated vapor of supplying with via steam supplying pipe 20 condensation in middle pressure drum 12, consequently, under the poorest condition, the situation of pressing the water level of drum 12 sharply to rise in may occurring due to the saturated vapor amount of supplying with.On the other hand, by water separator 24 is set, make the water level in middle pressure drum 12 only be subject to the impact by water separator 24 isolated liquid.Therefore, can make the fluctuation of water table in middle pressure drum 12 minimize.
In addition, water level in middle pressure drum 12 is controlled by three elements (water level, water output, generation vapor volume) conventionally, but in the present embodiment, by measure from high pressure drum 11 to the vapor volume of the saturated vapor supplied with of pressure drum 12, can to high pressure drum 11, middle pressure drum 12 all with conventionally similarly carry out boiler drum water level control.In addition, as described above, by water separator 24 being located in the upstream side or middle pressure drum 12 of middle pressure drum 12, can make the fluctuation of water table in middle pressure drum 12 minimize, therefore, also can make to minimize to the running variation that has or not the middle pressure drum 12 causing of the supply of the saturated vapor of middle pressure drum 12.
The action effect of present embodiment is described below.
In order to increase the steam total amount of supplying with to the cooling system towards gas turbine 3, different from present embodiment, as shown in the equipment 10 of the corresponding technology of Fig. 3, consider to use the high compressed steam being produced by high-pressure system 6.That is, by high compressed steam pipe 17 branches from high-pressure system 6 to steam turbine 4, and high compressed steam is guided to desuperheater 31, high compressed steam is carried out to desuperheat, decompression.And, supplied with to the cooling system of gas turbine 3 via steam pipe 32 and middle pressure steam pipe 19 by desuperheat, post-decompression high compressed steam.But, according to the method, although the steam that can not make the cooling system from medium voltage network 7 to gas turbine 3 supply with increases, specially carry out desuperheat, decompression to the steam of high temperature, high pressure, such desuperheat technique probably causes the reduction of device efficiency.
In addition, also consider not extract the saturated vapor of low temperature out from high pressure drum 11 as the situation of the cooling water of gas turbine 3 from needing the high-pressure system 6 of desuperheat technique.But, from high pressure drum 11 extract saturated vapor out and reduce pressure produce saturation water, the water of this generation may cause damage to the equipment of back segment, pipe arrangement, be difficult to adopt.
On the other hand, according to present embodiment, the backward middle pressure drum 12 of saturated vapor decompression of high pressure drum 11 is supplied with, in middle pressure drum 12, carried out carbonated drink separation.And, in not changing, press the control of drum 12 self compared with previous methods, in use, press the cooled vapor of steam as gas turbine.Now, do not adopt the design that suppresses high compressed steam amount and middle pressure vapor volume is increased, increase and can make that gas turbine 3 is carried out to cooling steam.Therefore, middle pressure vapor volume increased and do not suppress the high compressed steam amount higher to the contribution degree of equipment performance, can form comparatively economic heat recovery boiler 2.In addition, can reduce coolingly with water droplet contained in steam, vaporific water, therefore, being exposed in tail pipe cooling system under high heat load etc., can avoid the fault being caused by thermal shock etc.
It should be noted that, in the present embodiment, illustrated high pressure drum 11 and middle pressure drum 12 are linked and from high pressure drum 11 to pressure drum 12 supply with saturated vapor, make the situation of the vapor volume increase being generated by medium voltage network 7 with this steam, but the present invention is not limited to this.For example, system from low pressure drum 13 to other equipment classes that supply with steam from, also can apply the present invention.In the case, by high pressure drum 11 and low pressure drum 13 are linked or by middle pressure drum 12 link with low pressure drum 13, from high pressure drum 11 or pressure drum 12 supply with saturated vapor to low pressure drum 13, thereby the vapor volume being generated by low service system 8 is increased.
Symbol description
1,10 equipment
2 heat recovery boilers
3 gas turbines
4 steam turbines
5 re-heating subsystems
6 high-pressure systems (the first system)
7 medium voltage networks (second system)
8 low service systems
11 high pressure drums (the first drum)
In 12, press drum (the second drum)
13 low pressure drums
14 waste gas are supplied with road
15 cold reheat steam pipes
16 high temperature reheat steam pipes
17 high compressed steam pipes
18 low-pressure steam pipes
In 19, press steam pipe (the first stream)
20 steam supplying pipes (the second stream)
21 control valves (vapor volume regulating mechanism)
22 flowmeters
23 throttle orifices
24 water separators
25 control valves
31 desuperheaters
32 steam pipes
Claims (4)
1. a gas turbine cooling system, it possesses:
Gas turbine;
Heat recovery boiler, its have carry out heat exchange with the used heat from described gas turbine and produce the first system of the first steam, to described the first system for the first drum of feedwater and steam, carry out heat exchange with the used heat from described gas turbine and produce than the second system of the second steam of described the first steam low pressure, the second drum to described second system for feedwater and steam;
The first stream, it is connected described second system with the cooling system of described gas turbine, supply with described the second steam from described second system to described cooling system;
The second stream, it is connected described the first drum with described the second drum, supply with the saturated vapor in described the first drum from described the first drum to described the second drum.
2. gas turbine cooling system according to claim 1, wherein,
Described gas turbine cooling system also possesses vapor volume regulating mechanism, and the state of cooling of this vapor volume regulating mechanism based on described gas turbine is adjusted at the vapor volume of the described saturated vapor flowing in described the second stream.
3. gas turbine cooling system according to claim 1 and 2, wherein,
Be provided with water separator in the downstream of described the second stream and in the upstream of described the second drum or described the second drum.
4. a gas turbine cooling means, is the gas turbine cooling means of gas turbine cooling system,
Described gas turbine cooling system possesses:
Gas turbine;
Heat recovery boiler, its have carry out heat exchange with the used heat from described gas turbine and produce the first system of the first steam, to described the first system for the first drum of feedwater and steam, carry out heat exchange with the used heat from described gas turbine and produce than the second system of the second steam of described the first steam low pressure, the second drum to described second system for feedwater and steam
Described gas turbine cooling means possesses:
Cooling system from from described second system to described gas turbine is supplied with the step of described the second steam;
Supply with the step of the saturated vapor in described the first drum from described the first drum to described the second drum.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2011201856A JP5901194B2 (en) | 2011-09-15 | 2011-09-15 | Gas turbine cooling system and gas turbine cooling method |
| JP2011-201856 | 2011-09-15 | ||
| PCT/JP2012/073274 WO2013039088A1 (en) | 2011-09-15 | 2012-09-12 | Gas turbine cooling system, and gas turbine cooling method |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103975143A true CN103975143A (en) | 2014-08-06 |
| CN103975143B CN103975143B (en) | 2017-03-15 |
Family
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201280044710.3A Expired - Fee Related CN103975143B (en) | 2011-09-15 | 2012-09-12 | Gas turbine cooling system and gas turbine cooling method |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US20140338362A1 (en) |
| EP (1) | EP2752566B1 (en) |
| JP (1) | JP5901194B2 (en) |
| KR (1) | KR101520238B1 (en) |
| CN (1) | CN103975143B (en) |
| WO (1) | WO2013039088A1 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20150075450A1 (en) * | 2013-09-13 | 2015-03-19 | Uop Llc | Heat recovery from a high pressure stream |
| KR101801686B1 (en) | 2016-07-28 | 2017-11-27 | 두산중공업 주식회사 | Apparatus and method for cooling exhaust gas |
| CN114607477B (en) * | 2022-04-01 | 2023-08-01 | 邹平滨能能源科技有限公司 | Rapid cooling method for unit turbine |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0978636A1 (en) * | 1996-07-24 | 2000-02-09 | Mitsubishi Heavy Industries, Ltd. | Combined cycle power plant |
| CN1259618A (en) * | 1998-10-20 | 2000-07-12 | 瑞典通用电气－布朗－博韦里股份公司 | Turnine and its operation method |
| JP2001027133A (en) * | 1999-07-13 | 2001-01-30 | Mitsubishi Heavy Ind Ltd | Steam generating facility and turbine generating facility |
| US6220013B1 (en) * | 1999-09-13 | 2001-04-24 | General Electric Co. | Multi-pressure reheat combined cycle with multiple reheaters |
| JP2003013708A (en) * | 2001-06-27 | 2003-01-15 | Mitsubishi Heavy Ind Ltd | Turbine equipment |
Family Cites Families (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3751886A (en) * | 1971-08-31 | 1973-08-14 | Westinghouse Electric Corp | Vertical steam drum |
| US3965675A (en) * | 1974-08-08 | 1976-06-29 | Westinghouse Electric Corporation | Combined cycle electric power plant and a heat recovery steam generator having improved boiler feed pump flow control |
| US4572110A (en) * | 1985-03-01 | 1986-02-25 | Energy Services Inc. | Combined heat recovery and emission control system |
| JPH0443803A (en) * | 1990-06-08 | 1992-02-13 | Toshiba Corp | Control method for combined cycle power plant |
| DE59205446D1 (en) * | 1991-07-17 | 1996-04-04 | Siemens Ag | Process for operating a gas and steam turbine plant and plant for carrying out the process |
| DE69634019T2 (en) * | 1995-09-22 | 2005-11-03 | Kabushiki Kaisha Toshiba | Power plant with combined cycle |
| DE19609912A1 (en) * | 1996-03-14 | 1997-09-18 | Asea Brown Boveri | Process for operating a power plant |
| JP3776516B2 (en) * | 1996-07-24 | 2006-05-17 | 三菱重工業株式会社 | Combined cycle power plant |
| WO1999037889A1 (en) * | 1996-07-24 | 1999-07-29 | Mitsubishi Heavy Industries, Ltd. | Combined cycle power plant |
| JP3500020B2 (en) * | 1996-11-29 | 2004-02-23 | 三菱重工業株式会社 | Steam cooled gas turbine system |
| JP3800384B2 (en) * | 1998-11-20 | 2006-07-26 | 株式会社日立製作所 | Combined power generation equipment |
| JP4698860B2 (en) * | 2000-04-18 | 2011-06-08 | 三菱重工業株式会社 | Turbine steam control device |
| JP4395275B2 (en) * | 2001-07-05 | 2010-01-06 | 三菱重工業株式会社 | Operation method of combined plant |
| US6851265B2 (en) * | 2002-02-19 | 2005-02-08 | Siemens Westinghouse Power Corporation | Steam cooling control for a combined cycle power plant |
-
2011
- 2011-09-15 JP JP2011201856A patent/JP5901194B2/en not_active Expired - Fee Related
-
2012
- 2012-09-12 KR KR1020147006649A patent/KR101520238B1/en not_active Expired - Fee Related
- 2012-09-12 US US14/344,465 patent/US20140338362A1/en not_active Abandoned
- 2012-09-12 EP EP12832650.1A patent/EP2752566B1/en not_active Not-in-force
- 2012-09-12 CN CN201280044710.3A patent/CN103975143B/en not_active Expired - Fee Related
- 2012-09-12 WO PCT/JP2012/073274 patent/WO2013039088A1/en active Application Filing
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0978636A1 (en) * | 1996-07-24 | 2000-02-09 | Mitsubishi Heavy Industries, Ltd. | Combined cycle power plant |
| CN1259618A (en) * | 1998-10-20 | 2000-07-12 | 瑞典通用电气－布朗－博韦里股份公司 | Turnine and its operation method |
| JP2001027133A (en) * | 1999-07-13 | 2001-01-30 | Mitsubishi Heavy Ind Ltd | Steam generating facility and turbine generating facility |
| US6220013B1 (en) * | 1999-09-13 | 2001-04-24 | General Electric Co. | Multi-pressure reheat combined cycle with multiple reheaters |
| JP2003013708A (en) * | 2001-06-27 | 2003-01-15 | Mitsubishi Heavy Ind Ltd | Turbine equipment |
Also Published As
| Publication number | Publication date |
|---|---|
| CN103975143B (en) | 2017-03-15 |
| JP5901194B2 (en) | 2016-04-06 |
| JP2013064328A (en) | 2013-04-11 |
| WO2013039088A1 (en) | 2013-03-21 |
| KR20140059810A (en) | 2014-05-16 |
| US20140338362A1 (en) | 2014-11-20 |
| KR101520238B1 (en) | 2015-05-13 |
| EP2752566A1 (en) | 2014-07-09 |
| EP2752566A4 (en) | 2015-05-06 |
| EP2752566B1 (en) | 2018-05-30 |
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Address after: Kanagawa Prefecture, Japan Patentee after: Mitsubishi Power Co.,Ltd. Address before: Kanagawa Prefecture, Japan Patentee before: MITSUBISHI HEAVY INDUSTRIES, Ltd. |
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| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20170315 |